Printing telegraph apparatus



Dec. 19, 1961 R. w. NORDIN PRINTING TELEGRAPH APPARATUS 8 SheetsSheet 1 Filed May 13, 1958 INVENTOR ROBERT W. NORDIN ATTORNEY PRINTING TELEGRAPH APPARATUS Filed May 13, 1958 8 Sheets-Sheet 2 INVENTOR ROBERT W. NORDI N BMQQ AT TQRNEY FIG. 2

Dec. 19, 1961 R. w. NORDIN I 3,014,094

PRINTING TELEGRAPH APPARATUS Filed May 13, 1958 8 Sheets-Sheet 3 INVENTOR ROBERT W. NCRDIN Dec. 19, 1961 R. w. NORDIN PRINTING TELEGRAPH APPARATUS 8 Sheets-Sheet 4 Filed May 13, 1958 INVENTOR ROBERT W. NORDIN ATTORNEY Dec. 19, 1961 R. w. NORDIN PRINTING TELEGRAPH APPARATUS 8 Sheets-Sheet 5 Filed May 13, 1958 mmm mmm

Nov

own hmm mi? Ji Om QE INVENTOR ROBERT W. NORDIN BY W? ATTORNEY Dec. 19, 1961 w. NORDIN PRINTING TELEGRAPH APPARATUS 8 SheetsSheet 6 Filed May 13, 1958 FIG.

INVENTOR ROBERT W. NORDIN ATTOR Y Dec. 19, 1961 R. w. NORDIN 3,014,094

PRINTING TELEGRAPH APPARATUS Filed May 13, 1958 8 Sheets-Sheet 7 #BPULSE MARKIIY; r\

MA PACING FIG. I4

INVENTOR ROBERT W. NORDIN BY ATTORN Y Dec. 19, 1961 R. w. NORDIN PRINTING TELEGRAPH APPARATUS 8 Sheets-Sheet 8 Filed May 13, 1958 lNVENTOR ROBERT W. NORDIN ATTORNE path about wheel results in the printing 3,014,094 Patented Dec. 3.9, 39 61 PRINTING TELEGRAPH APPARATUS Robert W. Nordin, Sltoltie, El, assignor to Teletype Corporation, Chicago, fill, a corporation of Delaware Filed May 13, 1958, ser. No. 734,907 17 tjlaims. ll. 178-23) The present invention relates to printing telegraph aparatus and more particularly to telegraph printers of the page type.

The primary object of the invention is to provide a page printer of the type wheel class having a novel and compact arrangement conducive to lightweight construction.

Another object of the invention is to provide a page printer which emphasizes a simplicity of mechanisms, whereby the number and complexity of the component parts is reduced to a minimum.

A further object of the invention is to provide a readily portable page printer which is reliable and efiicient in operation, and which has the operating attributes inherent in certain extensively employed type bar printers.

Specifically, the telegraph printer according to the present invention is provided with a selecting mechanism of the type disclosed in US. Patent No. 2,339,313, issued to W. l. Zenner, but of improved construction and arrangement throughout. However, the printer disclosed herein comprises a stationary platen, having a type wheel carriage movable with respect therewith.

According to the embodiment of the invention disclosed, the type wheel is provided with four circumferential rows of characters, which characters are divided into an upper case group and a lower case group, said groups eing arranged on opposite send-circumferential is es of the type wheel.

The type wheel normally assumes a home or zero position peripherally with said home position centered between the two quadrants of a case group, depending upon which case group has been selected. The type wheel is then rotated either clockwise or counterclockwise from the home position to select a character in a quadrant in a manner similar to that disclosed in the aforementioned Zenner patent. The selection of the rows is likewise attained in the manner similar to that described in said patent.

A feature of the invention resides in a novel case shift mechanism which comprises a dirTerential gearing arrangement carried on the type wheel positioning shaft, which arrangement is ccoperable with the elevator or row determining means in predetermined character positions of the type wheel to effectuate the case shifting function.

Another feature of the invention resides in a novel arrangement for printing by means of a type wheel on page width paper supported by a cylindrical printing platen.

According to the disclosed embodiment of this feature of the invention the type wheel is rotatably supported on a frame pivotal y mounted on a shaft carried by the movable carriage. The shaft is associated with the selector mechanism or" printer and is rotatably indexed to selected positions by the selector mechanism in correspondence with received signals. The axis of the type wheel is parallel to the axis of the shaft and the type wl e is interconnected to the shaft by gearing to cause rotation of the type wheel under the control of the shaft to select a printing position of the type wheel. Printing is accomplished by means of a print hammer whic strikes supporting frame for the type wheel and rocks it about the t to carry the type wheel in an orbital hait until it strikes the paper supported Th ig of the paper by the type of a selected character. The foregoing and other objects of the invention will be apparent from the following description when taken in conjunction with accompanying drawingswherein:

FIG. 1 is a perspective view of the combined transmitting and receiving apparatus in accordance with the invention;

FIG. 2 is ,a side elevational view of the printer portion showing the selector mechanism and operating cam shaft;

FIG. 3 is a sectional view taken on line '33 of FIG. 2;

FIG. 4 is a sectional view taken approximately on line 4-4- of FIG. 2;

FlG. 5 is a fragmental elevational view of the orientation indicator;

F G. 6 is a sectional view mechanism;

FIG. 7 is a cross sectional view of the printer portion of the apparatus according to the present invention;

FIG. 8 is a sectional plan view of the printer portion, with parts broken away, to illustrate various internal mechanisms according to the invention;

showing the code bar reset FIG. 9 is a view taken along line 9-9 of FIG. 7; FIG. 10 is a sectional view taken on line lit-ll} of FIG. 9;

FIG. 11 is a perspective view of the stop members for.

determining the rotational positionment of the type wheel; FIG. 12 is a perspective view of the case shift mechanism for the type wheel;

FIG. 13 is an exploded perspective view of the case shift mechanism;

FIG. 14 is a sectional view of the assembled components of the case shift mechanism;

FIG. 15 is a schematic diagram illustrating the angular pesitioninent of characters on the type wheel;

FIG. 16 is a sectional view of a modified form of assembled components of the case shift mechanism;

FIG. 17 is a sectional view showing the line feed function mechanism;

FIG. 18 is a view taken on line 18-18 of FIG. 17;

FIG. 19 represents an alternate form of line feed mechanism; and

FIG. 20 is a view illustrating the Figures-Letters shift bar arrangement.

Having reference to FIG. 1 of the drawings, the numeral ill designates the telegraph apparatus generally, comprising a keyboard transmitting portion 12 and a printer portion 13. The selector assembly is designated by the reference numeral 14 and comprises a selector magnet 15 (FIGS. 1 and 4) suitably supported on a bracket attached to the side frame 16 of the apparatus 11. The selector mechanism 15 is essentially of the type shown and described in US. Patent No. 2,595,745, issued May 6, 1952, to W. J. Zenner. Extending from the printer side frame 16 is an armature mounting bracket 17 which carries, through the instrum'entality of a hinge 18, an armature pivot plate 19. To one end of the armature pivot plate I? is fastened one end of a spring 21, the other end of which is attached to an adjusting screw 22 appropriately mounted on the side frame 16. The function of spring 21 is to bias the armature pivot plate 19 counterclockwise (as viewed in FIG. 4) about the hinge 18 in response to a spacing condition impressed on the selector magnet 15. In response to a marking signal condition the magnet 15 becomes energized and armature 19 is attracted toward the pole piece 23, thereby stretching spring 21. The armature plate 19 thus oscillates in response to received code combinations of marking and spacing impulses.

Attached to and depending from armature 19 is a member 24 adapted to cooperate with a pair of marking and spacing sensing levers or sensors 25 and 26, respectively, and a start lever 27 (FIGS. 2 and 4). Levers 25 and 26 function in the manner disclosed in FIG. 3 of the aforementioned Patent 2,595,745 to provide an interlocking means to lock the armature 19 in marking or spacing position during the respective signal impulse interval under the control of a flutter cam 28 (FIG. 2) conformed in the manner of cam 17 shown in FIG. 3 of said Patent 2,595,745. The marking lever 25 is further provided with a depending portion 29 so fashioned as to cooperate with extensions 31 on the selector levers 32 to 36. Levers 25, 26, 27 and 32 to 36 are carried pivotally on the shaft 37. Levers 32 to 36 are each provided with an arm 38 which terminates in a hook-like portion adapted to coact with the hook-shaped extremity of a pull-bar 39 slidably mounted on a shaft 41, the forward ends of said pull bars 39 being supported in a guide comb 42.

Pull bars 39 are normally biased toward the pivot shaft 41 by individual springs 43. Each pull bar 39 is provided with a laterally directed portion '44 adapted to cooperate with the end of an associated latch arm 45 pivotally mounted on a pivot rod 46 carried in a bracket 47 attached to the side frame 16. Each arm 45 is adapted to cooperate in latching relation with a shoul der 48 on an associated selector bar of a series of selector bars 49l to 49-5. Selector bars 491 to 49-5 are provided near each end (only the right-hand end being shown in FIG. 4) with upwardly and leftwardly directed slots 54] whereby the selector bars 49-ll to 49-5 slidably carried on rods 51 in such a manner that individually associated springs 52 (FIG. 8), attached at one end to said selector bars and at the other end to frame 53, tend to urge said selector bars upwardly and leftwardly when they are released by their respective latch arms 45, as will presently appear. Latch arms 45 are normally biased clockwise by individual coiled springs 54 (FIG. 4) wrapped around a rod 55, and having one end coacting with the latch arm 45 and the other end anchored by a bracket 56.

Cooperating with the selector levers 32, and carried on a sleeve 57 mounted on a main shaft 58 are a series of selector cams 61 to 65 (FIGS. 2 and 4). Also carried on sleeve 57 are the flutter cams 28, a start-stop cam member 66, a reset cam 67 (FIG. 2), and a bail cam 68 (FIGS. 4 and 6). In the present embodiment of the invention, the start-stop cam member 66 comprises a cam portion 69 and a stop disc portion 71. The cam member 66 is designed for two-cycle operation; that is, a cycle of operation is etfectuated during each one-half revolution of the cam member 66. Therefore, the cam portion 69' is provided with two diametrically opposed notches 72, and disc portion 71 is provided with two diametrically opposed stop lugs 73.

Lugs 73 of the disc 71 are adapted to cooperate with the laterally directed end of a bell crank lever 74 mounted pivotally on a pivot stud 75 (FIGS. 2 and 4) carried on an orientation plate 76, PEG. 5. The plate 76 is adapted to rotate about the shaft 58, and clamping facilities 77 are provided to secure plate 76 to the side frame 78 when the proper orientation range is established in a manner well known in the art. The other arm of bell crank 74 is provided with a cam follower portion 79 cooperable with cam 69, and a laterally directed bifurcated portion 81 adapted to engage arm 82 of the start lever 27.

In the operation of the selector just described, the signal impulses are received over line wire 83 to operate the magnet accordingly. Since the normal stop condition of the line is marking (or current on the line) the magnet 15 is energized to hold its armature 19 in the attracted position, shown in FIG. 4. In this condition the shouldered extremities of levers 26 and 27 rest on the cross-bar 34 of depending portion 24. Lever 27 in this position is effective through its arm 82 to hold bell crank 74 in its counterclockwise position to hold the disc 71, and hence the cam sleeve 57 against rotation, in well known manner in start-stop operation. In response to this stop condition, the sensor is also held away from the edge of the cross-bar 84 by the flutter cam 28 thus permitting vibration of armature 19.

In response to a start condition of the line 83 (no current or spacing) the magnet 15 will become deenergized and release its armature 19 to cause cross-bar S4 to ride off the shoulder of sensor 27, thus permitting the sensor 27 to respond to the pull of its spring 85 (since its follower 79 is opposite the notch 72 in cam 69), thereby rotating bell crank 74 clockwise to become disengaged from lug 73 and permit the cam member 66 and cam sleeve 57 to rotate one-half revolution, thus initiating start-stop operation. It is observed that only the sensors 25 and 26, and lever 27 cooperate with the armature extension 24, and none of the selector levers 32 to 36 cooperate directly with the extension 24. Instead, the selector levers 32 to 36 cooperate with depending portion 29 of sensor 25. The earns 61 to are of similar earn contour but are displaced on the shaft 58 angularly so that the cam notches therein are disposed in a helically arranged series whereby coaction with the cam follower portions 86 will occur in a sequential manner as the series of cams 61 to 65 rotates in synchronism with the speed of code impulsing. Thus, the earns 61 to 65 will sequentially allow the levers 32 to 36 to respond to the pull of their respective springs 87 unless said levers 32 to 36 are blocked through the coaction of the sensor 25 and the cross-bar 84- of extension 24.

In timed relation with the receipt of the code impulses, the cam followers 86 in response to marking impulses will fall sequentially into the respective cam notches 91 in earns 61 to 65. Thus, when the cam follower 86 of the first selector lever 32 falls into its associated notch 91, the lever 32 will rotate clockwise in response to the pull of its spring 37 to permit the hook-shaped end 88 to engage the hook-shaped end 89 of its associated pull bar 39. Then, when the cam follower portion 86 cooperates with the cam lobe 92, the selector lever 32 is actuated counterclockwise, and since the end 38 is now engaging the end 89, the pull bar 39 will be actuated upwardly. Therefore, operation of pull bars 39 takes place pursuant to each impulse if the impulse is of marking nature, because in response to a marking impulse the magnet 15 will be held energized and the shouldered end of marking lever 25 will be unblocked, and portion 29 will be allowed to drop to permit levers 32 to 36 to engage the peripheries of their respective cams 61 to 65 to effectuate the aforementioned operation of the associated pull bar 39. On the other hand, if the signal impulse is of spacing nature, the armature 19 will be released, and therefore cross-piece 84 will block the clockwise movement of the marking lever 25, thereby preventing the engagement of pull bar 39, and thus the pull bar 39 will remain unoperated.

Pursuant to the permutative operation of pull bars 39, the portions 44 of the actuated ones thereof will trip the corresponding latches 44 out of engagement with the shoulders 48 of associated selector bars l91 to 49-5 upwardly and leftwardly, to effect predetermined selective operations, as will hereinafter be described. As shown in FIGS. 2 and 4, a U-shaped bail member 93 is mounted pivotally on shaft 41, which member 93 is provided with a cam follower arm 94 adapted to cooperate with the aforementioned reset cam 67, said bail 93 being biased clockwise (as viewed in PEG. 4) by a spring (not shown) to maintain follower arm 94 in contact with cam 67. Bail member 93 is provided with a T-shaped portion 95 having sidewardly directed arms which span the pull bars 39,

so that at a proper time in the selective operation, the

cam 67 will actuate the bail 93 in a clockwise direction (as viewed in FIG. 4) to disengage pull bars 39 from levers 33, the pull bars 39 then being returned to their normal position by springs 43.

In FIG. 6 is shown the mechanism for permitting the operation of selector bar's 49--1 to. 49-5 and for restoring said selector bars't'o their normal unselected position and comprises a bail 96 mounted pivotally on a pivot rod 97 carried in the bracket 47. Pivoted at 925 to bail 96 is an arm 99 normally urged in a clockwise direction by a spring 106. Arm @9 is provided with a shoulder 101 adapted to cooperate with a bail member 162 fixed to a shaft 103. Ann 99 is also provided with a cam surface 164 adapted to cooperate with a stud 1155 carried on trip bail member 106 which is freely carried on said shaft 1133. Trip bail 1136 is provided with an arm 1117 which is cooperable with the periphery of the bail cam 63 fixed to the cam sleeve 57. Bail 1%, which is U-shaped (as more clearly shown in FIG. 2) is also provided with an arm 1113 pivotally articulated through stud 1119 to the clutch trip bail 111 of a single revolution toothed-clutch 112. Bail 111 is carried freely on shaft 193 and is normally urged toward the clutch 112 by a spring 113.

Clutch 112 comprises a toothed driving portion 114- fixed to the main drive shaft 58 (FIGS. 1 and 2). Power for driving the shaft 58 is derived through gears 115, 116 and 117 from a motor 118. Cooperating with the driving portion 114 of clutch 112 is a toothed driven portion 119 which has integral therewith a flange portion 121 provided with a projection 122 which coacts with an inclined cam surface 123 on bail 111 to effectuate the disengagement of clutch 112 in a manner Well known in the art.

Driven portion 119 of clutch 112 is provided with a hub portion 124 having therein a pair of spline-ways 125 adapted to receive a pair of splines 126 integral with the hub portion 127 of a cam sleeve 128, which carries integrally thereon a flange 129, and cams 131 and 132. Encircling the hub portions 124 and 127 and positioned between fianges 121 and 129 is a compression spring 133 which tends to urge the cam sleeve 128 leftwardly (as viewed in FIG. 2) against a thimble 134 on shaft $3 spaced between sleeve 128 and a clutch 135 securely clamped to shaft 53. Spring 133 also tends to urge the driven portion 119 of clutch 112 rightwardly into engagement with driving portion 114 when the clutch is tripped, as will presently appear.

Having reference to FIGS. 2 and 3, earn 133 is substantially elliptical in shape and cooperates with a pair of follower rollers 136 and 137 carried on a bell crank lever 138 fixed to the shaft 103. It is to be noted that bell crank 13% (FIG. 3) and hail 102 (FIG. 6) are both fixed to the shaft 193 for simultaneous actuation, as will presently appear. Also, bell crank 138 has aflixed thereto an arm 139 for controlling the printing operation, to be hereinafter described.

As previously described, the receipt of the start impulse initiates rotation of the selector cam sleeve 57 to control the selec ion of selector bars t--1 to 49- 5. In proper timed relation, the cam 63 on said cam sleeve 57 is effective through arm 1tl7 (Flu. 6) to rock the bail 1116, to in turn, through stud 109, rock bail 111 to disengage lug 122 therefrom to permit the engagement of portions 114 to 119 of clutch 112 to initiate the rotation of cam sleeve 128. Simultaneously therewith, the rocking of bail 1 56 caused the stud 1115 thereon to strike the cam surface 1134 to effect the disengagement of arm 9% from the bail 1G2, whereupon the bars 4% which were unlatched by the pull bars 39 were permitted to respond to the pull of their respective springs At the same time, the projections 1 51 on the selector oars 4 9-1 to 49-'5 acted upon bail 6 to rotate said bail 96 counterclockwise, thereby carrying arm 9 leftwardly until depending portions 142 of arms 99 were arrested by a stop pin or stud 143. Due to the shape of cam 133 (FIG. 3), oscillatory movement is imparted through bell crank 138 and shaft M3 to the bail member (FIG. 6) so that bail 1&2 in its counterclockwise position will pick up the shoulders 101 of arms $9 of the previously released selector oars 49-1 to 49-4) to return said selector bars to their latched position in latching engagement with latches 45.

Selector cam sleeve 57is rotated by shaft 53 through 174, as viewed in Pro. 12, to

the instrumentality of clutch (FIG. 2). Clutch135 comprises a housing portion 144 which is securely fixed, by clamping means 145 integral therewith, to shaft 58. Thus, housing 144 constitutes the constantly rotating part of the clutch, and through a pair of friction means 146, said rotation is communicated through a sleeve member 147 to the cam sleeve 57.

Referring to FIG. 7, the selector bars 49-1 to 49-5 control the selective positionments of the type Wheel 1511, as well as the selection of a plurality of function levers 152 which are mounted pivotally on a rod 153 and biased counterclockwise by individual springs 154 into selective cooperation with the coded bottom edges of said selector.

bars. Function levers 152 cooperate with a bail blade member 155 integral with a cradle portion 156 pivotally mounted on said rod 153 (FIGS. 7 and 8). As seen in FIG. 7, the upper end of a link 157 is provided to the bail blade 155, and the lower end of said link 157 is pivotally connected to the end of a lever arm 158 clamped to ashaft 15'? (FIG. 3) to which is also clamped'a lever 161 carrying at its extremity a cam follower roller 162 cooperable with the cam 132. Springs 154, through lever 152, bail E5, link 157, and levers 1'58 and 161 hold the roller 162 against the periphery of cam 132. Thus, cam 132, through said interconnection with bail 155 is effective to control the movement of function levers 152 toward and away from the bottom edge of the selector bars 49-1 to 495.

Having reference again to FIG. 7, the printer unit, designated generally as 11, is provided with a rockable platen 163 stationarily mounted therein, and a type wheel carrier, generally indicated 15 i, movable-with respect to said platen to effect character spacing. The type wheel carrier 164 is movable as a unit across the printer unit and is provided with a pair of rollers 165 cooperable with a track member 165 appropriately carried on a cross bar 167 of the printer unit; and also a pair of grooved rollers 163 cooperable with a cylindrical track 169 suitably supported in the printer.

The type wheel carrier 164, in accordance with the specific embodiment of the invention disclosed herein, comprises a platform 171 disposed substantially at a 45,- degree angle between said pairs of rollers 165 and 168, to which is fixed a flanged sleeve member 172 of substantial length suitable to support and guide a type wheel positioning shaft 173 for slidable movement therein. Shaft 173 is appropriately positioned with respect to the platen 163 so as to bring the type wheel 157 into proper print ing relationship with the platen. According to the present invention, the type wheel 157 is rotatably carried in a U-shaped bracket 17 i mounted pivotally on the shaft 173 (FIGS. 1 and 7). Bracket 17 iis normally biased by a spring 175 to maintain the type wheel normally out of printing engagement with said platen 163. Fixed to type wheel 157 (FIG. 1) is a gear 176 which meshes with an idler gear 177 which in turn meshes with a gear 173 fixed to the shaft 173, through which gear train, rotational movement is imparted to type wheel 15? to effect the selective positionment angularly of the type characters on the type wheel, as will hereinafter appear.

To effect printing, when the desired type character is presented to the printing point, a print hammer 179, poised in latched position above the free end of bracket 174, is released at the proper time to strike bracket 17% sharply to cause the type wheel to impinge against the inking ribbon 181 to produce a printed record on the recording material 182 (FIG. 1).

During the counterclockwise movement of bracket carry the typewheel in an orbital path about gear 178 from the normal position of thetypewheel to the printing in acounterclockwise direction about its axis, rolls about gear 178 which is then stationaryand in turn rotates gear 176 and typewheel 151-clockwise about their common axis thereby exactly off-setting a change in initial position, gear 177, rotating i i shown in FIG. 7. Then,

orientation of the typewheel 151 with respect to the platen 163, that tends to result from pivotal movement of frame 174 about its axis. Accordingly, during the movement of the typewheel from normal position to printing position the orientation of the typewheel remains unchanged and the vertical row of characters on the surface of the typewheel that has been presented in confronting relation to the platen by the selector mechanism prior to the operation of bracket 174 by print hammer 1'79 remains in confronting relation to the platen throughout the rocking of bracket 174.

. Having reference to FIGS. 2 and 3, it is recalled that lever 138, controlled by cam 131, is provided with an arm 139. Arm 139 (FIG. 3) is connected pivotally to the lower end of a link 1%, the upper end of which is pivotally connected to the horizontal arm of a bell crank lever184 of U-shaped conformation fixed to the end of a shaft 185 journled in side plate 16. At its opposite end, shaft 185 is also journaled in the opposite side plate, and has fixed to said opposite end an arm (not shown) similar to the vertical arm of bell crank 134. Then, pivotally connected to the vertical arm of bell crank 184 and similady to the arm at the opposite end of shaft 185 are the right ends (as viewed in FIG. 2) of a pair of operating links 186 (only one being shown), the left ends of which are pivotally articulated to the ends of an operating track member 187, shown in section in FIG. 7. Thus, when the cam 131 is rotated, the bell crank 138 will oscillate, thus causing through arm 139 and link 133, the bell crank 184 to oscillate. Since bell crank 184, and the aforementioned arm at the opposite end of shaft 185 are fixed to said shaft 185, links 186 are caused to reciprocate together to impart a rightward and leftward (to and fro) motion to the track member 187.

Since one of the functions of the operating track member 187 is to control the printing operation'during the entire movement of the traveling type wheel carriage 164 along tracks 166 and 169, the main operating lever 188 thereof is provided with a pair of grooved rollers 1S9 suitably positioned substantially on opposite sides of track 187. Lever 188 is pivotally carried on a pivot rod 191 suitably mounted in the carriage 164, and is of U-shaped conformation and is provided with a pair of arms 192 adapted to operate with a member 193 fixed to the end of the shaft 173. Member 193 is normally held against the arms 12 by a pair of springs 194 distended between said member 193 and the platform 171 of the carriage 164, so that as the lever 188 is rocked in a counterclockwise direction by member 187, the springs 194 will urge the type wheel positioning shaft 173 upwardly (in a direction axial to said shaft 173) various distances governed by a plurality of stop portions 221, 222 and 223, as will hereinafter be described.

Lever 188 is also provided with an upwardly directed arm 195 to the extremity of which is connected pivotally a control arm 1% for the control of the print hammer 179. Hammer 179 is mounted on a bail member 197 pivotally supported on a shaft 198% fixedly supported in the carriage 164. Member 197 is biased clockwise by a spring 199 coiled about the shaft 198 to effect the printing operation, as will presently appear. Bail member 197 is provided with a depending arm 2191 which carries adjacent its extremity an inwardly directed stud 2132 adapted to cooperate with an open-ended slot 203 in the extremity of said arm 1%. Arm 1% is also provided with a second inwardly directed stud 264 which is adjustably clamped in a slot 205 in said arm. Stud 294 cooperates with a depending arm 206 of a latching member 207 pivotally supported on a bracket 208 attached to the platform 171. vLatching member 207 is provided with a latch arm 269 which cooperates with the printing bail member 197.

In the operation of the printing mechanism, it is assumed that the parts are in their relative positions, as when the clutch 112 (FIG. 2)

tripped to cause cam 131 (FIG. 3) to rotate 180 degrees (one cycle) the lever 13% will oscillate once to impart a rightward and then a leftward motion to link 1% (FIG. 2), which motion in turn is imparted to the operating track member 187, to impart, first, a counterclockwise movement to lever 13% (FIG. 7), and then a clockwise (return) movement thereto. During the counterclockwise motion of lever 188, the arm 196 is actuated leftwardly (FIG. 7) to cause stud 294 to impinge against the arm 2% to rock the latch lever 207 clockwise to disengage the latch arm 299 from the bail 197. Spring 199 will then cause hammer 179 to rotate in a clockwise direction to impinge sharply against the bracket 174 to throw the type wheel 151 (which has been previously selectively positioned, as will hereinafter appear, to print the desired character) against the platen 163 to effect printing. It is to be noted that prior to the time that stud 204 strikes arm 2%, the slot 203 will have moved leftwardly sufficiently to have cleared the stud 262 to permit the sharp clockwise motion of hammer 179 under the influence of spring 199. Now, track 187, upon its leftward movement will cause lever 13% to rotate clockwise to cause arms 192 to return the type wheel positioning shaft 173 to its lowest position, and at the same time arm 1% is moved rightwardly to permit spring 211 to bring latch arm 209 into latching relation with bail H7 as the slot 2% of arm 196 is effective to impart counterclockwise rotation to bail 197 to effectuate said latching engagement. Thus, type wheel 151 has been lowered sufficiently to provide visibility of the printed record, and the print hammer 179 has again become poised for a succeeding printing operation.

The type wheel positioning mechanism, having reference to FIGS. 7, 10 and 11, comprises three operational sections. The first section concerns vertical positioning of the type wheel 151 as controlled by the selector bars 49-1 and 49-2. The second section concerns direction of type wheel rotation as controlled by the selector bar 49-3, and the third section concerns the amount of rotation as controlled by selector bars 49-4 and 49-5.

Selector bars 49-1 and 49-2 cooperate with sensing levers 212 and 213, respectively. Similarly, selector bars 49-4 and 49-5 cooperate with sensing levers 214 and 215, respectively. Selector bar 49-3 cooperates with a sensing lever 216 to control the direction of rotation of the type wheel 151. Levers 212, 213 and 216 are mounted pivotally on a pivot shaft 217, and levers 214, 215 are mounted pivotally on shaft 218. The confronting pairs of sensing levers 213 and 214, and 212 and 215 are attrahently biased by a spring 219, one common to each pair. Selector bars 49-1 to 4-5 are shown in FIG. 7 in their uppermost position, in which iposition sensing levers 212, 213 and 216 are held in their counterclockwise position, and sensing levers 214 and 215 are held in their clockwise position. Sensing lever 213 is provided with the aforementioned reverted end or stop portion 222, and sensing lever 212 is provided with the reverted end or stop portion 223. Sensing levers 212 and 213 are each provided with an arm 220 adapted to cooperate with an arm 224, spanned thereacross, of a lever 225 also carried pivotally on shaft 217. Lever 225 is provided with the aforementioned reverted end or stop portion 221.

In the normal rest condition of the printer, the selector bars 49-1 to 49-5 are held in their lowermost I positions by the bail (FIG. 6) to thereby cause the sensing levers 212, 213 and 225 to be held in their clockwise positions by the springs 219 (FIG. 7), and the bars 214 and 215 to be held in their counterclockwise positions by the same springs. Thus, with levers 212, 213 and 225 held normally in their clockwise position the stop portions 221, 222 and 223 thereof are normally positioned in the path of a striker portion 226 of member 193 (more clearly shown in FIG. 12). The type wheel 151 and its associated parts move vertically during 9 each cycle, returning to a home or lowest position at the end of the cycle.

Hence, with selector bars 491 and 49-2 in their lowermost or unselected position the levers 212 and 213 assume their clockwise positions, so that the stop portions 22 222 and 223 are all in the path of striker 225 and accordingly, the type wheel 151 will be elevated to bring row 227 thereof into printing position With relation to platen 163. Then, when selector bar 49-1 alone is selectively unlatched by its latch 45 it will rise to its uppermost position to rotate sensing lever 212 counterclockwise thereby moving its stop portion 223 out of the path of striker 226, and at the same time, because of the cooperative relationship between arm 22d) of lever 212 and arm 224 of lever 225, also move stop portion 221 out of said path, thereby exposing stop portion 222 of lever 213 solely in said path, the striker 226 will be permitted under the influence of springs 194 (when released by lever llSS) to strike against stop portion 222 to bring row 228 of the type Wheel 151 into the printing position. Now, when selector bar 492 alone is selected it will rise to its uppermost position to rotate sensing lever 213 counterclockwise, thereby moving its stop portion 222 out of the path of striker 226 and simultaneously, because of the cooperative relation between arm 220 of lever 233 and arm 224 of lever 225, also move stop portion 221 out of said path, thereby exposing stop portion 223 of lever 212 solely in said path, the striker 226 Will be permitted to strike against stop portion 223 to bring row 229 of the type wheel 151 into the printing position. Finally, when both selector bars 42-1 and 4-92 are simultaneously selected, they will rise to their uppermost position to rotate both sensing levers 212 and 213 counterclockwise, thereby moving their stop portions 223 and 222 out of the path of striker 226, and simultaneously, because of said cooperative relation between arms 220 and 224, stop portion 221 will also be moved out of the path of striker member 22s thereby permitting striker member 226 to impinge against the aligned shoulders 232 of said sensing levers to bring row 231 of the type wheel 151 into printing position.

As previously mentioned, the sensing levers 214 and 215 control the rotational positionment of the type wheel 151. Levers 214 and 215 are provided with vertical arms 233 and 234-, respectively (FIGS. 7 and 11), adapted to cooperate with stop members 235, 23s and 23,7 slidably carried in a combination guide and fixed-stop mem ber 23% mounted on the platform 171. Cooperably related to the stops 235, 236 and 237 are a pair of rack members 239 and 241 (FIG. guided by suitably located posts 24s, the rack portions of which mesh with a type wheel positioning gear 242 operably carried on the type wheel shaft 173. The lower ends of rack members 239 and 241 (as viewed in FIG. 10) terminate in striker or stabber portions 2 3 and 244 (respectively) cooperably related to the stop members 235, 236 and 237. Racks 239 and 241 are provided with shoulders 245 and 2%, respectively, which are adapted to cooperate with the bail blade 24? of a bail member 248 carried slidably on a shaft 249 suitably journaled in a Ll-shaped memoer 251 carried pivotally on the shaft 121. Member 251 is normally biased counterclockwise (as viewed in FIG. 7) by a coiled spring 252 encircling the shaft 191, which holds said member 251 yieldably against a set screw 253 carried by the lever 188.

Although the bail 248 is shown in H6. =10 in a centralized position, it is in actual practice positioned in such a manner that the bail blade 247 is coacting with either of the shoulders 245 or 245. The bail 245 is shifted on the shaft 249, to cooperate with either shoulder 245' or 2 26, under the control of the selector bar 493. As shown in FIG. 7, the selector bar -69-3 cooperates with the lever 21:? pivotally mounted on the shaft 217, which lever is provided with an arm which is articulated pivot- Thus, if the ally with an arm 254 (FIG. 10) of a bell crank lever 255 pivoted at 256 to the underside of the platform 171. Lever 255 is provided with an arm 257 pivotally articulated to the bail member 248 at 258. Thus, when the selector bar 49-41 is in its lowermost position, the lever 2% assumes its clockwise position (as viewed in FIG. 7) to cause bell crank 255 to assume its clockwise position (FIG. 10), to cause bail 248 to be shifted to its righthand position to bring bail blade 247 into cooperative relation with shoulder 246.

Then, when the operating lever 188 is rocked counterclockwise (FIG. 7) in its cycle of operation, as previously described, member 251 is similarly actuated (due to spring 252), thereby causing bail blade 247 of bail member 248 to actuate the rack member 241 upwardly (as viewed in FIG. 10) to rotate the gear 242 in a counterclockwise direction, to cause, in turn, the rack member 239 to be moved downwardly, to cause the striker portion 243 of rack member 239 to impinge against a selected stop member 235, 236 or 237. When the lever 138 is returned to its clockwise position (FIG. 7), the member 251 Will also be similarly rotated positively, through set screw 253, to cause rack member 241 to be moved downwardly because of the pressure applied at the end thereof by the roller 364 carried on the end of shaft 249, to rotate the type wheel 151 to its home position with the rack members 239 and 241 positioned as shown in FIG. 10.

Similarly, when the selector bar 43 is in its uppermost position, the lever 216 assumes its counterclockwise position (as viewed in FIG. 7) to cause the bell crank 255 to assume its counterclockwise position (FIG. 10) to cause bail 248 to be shifted to its left-hand position on shaft 249 to bring the bail blade 247 into cooperative relation with shoulder 245 of rack member 232. Then, when the operating lever 183 is rocked counterclockwise (FIG. 7) in its cycle of operation, as previously described, member 251 is similarly actuated under the action of its spring 252, thereby causing bail blade 247 to actuate rack member 239 upwardly thereby causing gear 242 to rotate in a clockwise direction to move rack member 239 downwardly to cause striker portion 24-3 of rack member to abut against a selected stop member 235. 236 or 237.

Having reference to FIG. 15, it is observed that each row (22'7-23l) of the type wheel 151 is provided with sixteen characters 2521, arranged with four characters in each quadrant. Also, the figures characters are included in one 189 portion, and the letters characters are included in the other portion. As indicated schematically in Fl'G. 15, the type wheel 151 normally assumes a home or zero position peripherally, and is rotated either clockwise or counterclockwise depending upon the nature of the signal impulse which controls the selective positionment of selector bar 49-3. Hence if the No. 3 impulse of the code signal is of marking nature the selector bar 49-3 will assume its uppermost position (FIG. 7) so that sensing lever 226 will be actuated in a counterclockwise direction, thereby causing lever 255 (FIG. 10) to be also actuated in a counterclockwise direction to bring bail blade 247 into cooperative relation with shoulder 245. Thus, when bail 251 is actuated rearv/ardly (as viewed in FIG. 10), the rack member 239 will impart clockwise rotation to the gear 242, and hence to the type wheel 151, to bring one of the characters 261 in quadrant 262 into printing position, which is coincident with the point marked home position (FIG. 15).

The amount of rotation imparted to the gear 242 (and hence type wheel 151) is governed by the stop members 235, 235 and 237. Stop member 237 is normally biased into stop position by individual leaf spring 253, while stop members 2155 and 23 5 are articulated to arms 233 and 23 respectively, for. p ositive movement therewith. fourth and fifth impulses of the code signal are of spacing nature, the selector bars 5-4 and 49-5 will assume their lower positions, and the sensing levers 21 and 215 will assume their counterclockwise positions so that the stops 235, 236 and 237 are held in their in ward or stop positions, and the stabber 244 will impinge against stop 237 and the type wheel will be rotated to bring the first character in the qudrant (indicated lettersmarking) into printing position. Now, if the fourth impulse is of marking nature and the fifth impulse is of spacing nature, the selector bars 49-4 and 495 will assume their upper and lower positions, respectively, so that sensing lever 214 actuated by bar 4@4- will move the stops 237 and 235 out of the path of stabber 244 (or 243), lever arm 233 being ineffective to move stop 236 because of opening 26? therein, thereby permitting stabber 244 to impinge against stop 236, allowing the type wheel 151 to rotate to bring the second character in said quadrant into printing position. if the fourth impulse is of spacing nature and the fifth impulse is of marking nature, the selector bars l4 and 49-5 will assume their lower and upper positions, respectively, so that sensing lever 215 will move the stops 237 and 236 out of the path of stabber 244 (or 243), lever arm 234 being ineffective to move the stop 235 because of opening 265 therein, thereby permitting stabber 244 to impinge against stop 235, allowing the type wheel 151 to rotate to bring the third character in said quadrant into printing position, Lastly, if the fourth and fifth impulses are both of marking nature, the selector bars 49-4 and 49-5 will both assume their upper positions, so that all of the stops 235, 236 and 237 will now be moved out of the path of stabber 244 (or 243), thereby permitting the stabber 244 to impinge against the fixed stop 266, allowing the type wheel 151 to rotate to bring the last or fourth character in said quadrant into printing position.

Conversely, if the No. 3 impulse of the code signal is of spacing nature, the selector bar 49--3 will assume its lower position so that sensing lever 216 will be actuated in a clockwise direction, thereby causing lever 255 to be also actuated in a clockwise direction to bring bail blade 247 into cooperative relation with shoulder 246. Thus, when bail 251 is actuated rearwardly the rack member 241 will impart counterclockwise rotation to the gear 242, and hence to the type wheel 151, to bring one of the characters 261 in quad-rant 267 into printing position.

The procedure of selecting the characters in the quad rant 267 is similar to that just described in connection with quadrant 262, except that the type wheel 151 is rotated counterclockwise, and the character selection is achieved through the cooperation between stabber 243 and stops 235, 236 and 237.

As previously indicated, the general theory of operation of the case shifting feature is to provide two 180- degree sectors on the type wheel 151. As indicated in FIG. 15, one sector contains the letters characters and the other sector contains the figures characters. As will presently appear, the purpose of the case shift mechanism according to the present invention is to rotate the type wheel 180 degrees, in response to a figures shift code signal or a letters unshift code signal.

The shift mechanism according to the invention cornprises a sleeve member 271 (FlGS. 12, 13 and 14) keyed to the type wheel positioning shaft 173. Member 271 has fixed thereto at one end thereof a bevel gear 272, andat the other end said sleeve 2'72 is associated with a collar member 2'13 integral to which is the aforementioned type wheel positioning gear 242. Also integral with the collar 73 and disposed oppositely to gear 242 is a bevel gear 27 i. Positioned between the confronting bevel gears 2'72 and 274-, and carried freely on the sleeve 271 between said confronting bevel gears is a sleeve member "275. i In the embodiment of the invention herein disclosed, the collar 273 and sleeve 275 are octagonal in their peripheral surface. Projecting radially from two diametrically op posits faces of sleeve 275 and in axial alignment with each other are a pair of studs 276 for mounting a pair of planetary gear members 277. In the embodiment shown in FIG. 13, gears 272 and 27 are of different pitch, and to agree therewith, the planetary gear members 277 are provided with two gear sectors 278 and 279 of different pitch diameters to mate with the gears 272 and 274, respectively, for the purpose hereinafter described. Thus, as noted in FIG. 14, the studs 276 are eccentrically located with respect to the distance between gears 2'72 and 274 to compensate for the difference in pitch diameters.

Referring to FIG. 13, the sleeve 275 is provided on a face intermediate the studs 276 with an outwardly extending sectorally shaped portion or impinging means 231. As shown in FIG. 14, the collar member 273 is detented to the sleeve 271 by a ball and spring device, comprising, as shown in FIG. 13, a pair of ball bearings 282 positioned in apertures located in diametrically opposite faces of the collar 273. Said ball bearings 282 are suitably retained by a U-shaped retaining spring member 283 adapted to straddle said collar 273, and having holes 284 of smaller diameter than the diameter of said ball bearings 282. Retaining spring 283 is appropriately guided by the flanges 285 of a guide member 286 which is securedto a face of said collar 273 intermediate said ball bearings 282 by a screw 287. Ball bearings 282 cooperate with a groove 280 in the sleeve 271 to provide a detenting action between sleeves 271 and 273.

Having reference to FIG. 12, there is pivoted at 283 on a bracket 289 secured to the bottom side of the platform 171, a blocking lever or inhibitor 291, which is normally biased in a clockwise direction by a spring 292 distended between an arm 293 of lever 2M and the hook portion 294 of a U-shaped slidable member 295. Member 2% is suitably guided by the coaction between its arm 296 and a guide slot in the platform 171, and is also provided with a latch portion 297 adapted to have latching relationship with the upper extremity of arm 298 of lever 291, as will presently appear. Arm 29% of lever 2.?1 is also provided with a locking portion 299 adapted to cooperate with the sector 231. Member 193 is provided with an arm 391, the extremity of which cooperates with the web portion of said U-shaped member 295. Arm 301 is provided at a predetermined distance from its extremity with a laterally extending portion 3%2 adapted to cooperate with the arm 293 of lever 291.

In the normal operation of the apparatus, the en tire shift mechanism carried on the sleeve 271 (FIG. 14) rotates with the type wheel shaft 173 as controlled by the positioning rack members 239 and 241. During the selection of each character, the type wheel 151 rotates to the printing position and then rotates back to the home position. When a figures shift or a letters shift code combination is received, the type wheel 151 is positioned in its extreme upward and rotary position, either in a clockwise or a counterclockwise direction from the home position, depending upon whether the lie. 3 impulse of the code signal is of marking or spacmg nature.

For example, if a figures shift code signal is received, wherein the No. 3 impulse of the code is of spacing nature, the bail 248 is shifted to the right (FIG. 10), and the rack 241 would be actuated rearwardly thereby to rotate the gear 242 in a counterclockwise direction (clockwise in FIG. 12) until the stabber 243 impinges against the fixed stop 266, as determined by the fact that the Nos. 4 and 5 impulses of the figures" shift code are of marking nature, and all of the stops 235, 236 and 237 have been withdrawn from the path of said stabber 243. Thus, the type wheel positioning shaft 1'73 has been rotated to its extreme rotary position counterclockwise (clockwise in FIG. 12). Also, since the Nos. 1 and 2 impulses of the figures shift are of marking nature the striker portion 226 (FIGS.

7 and 12) of member 193 will impinge against shoulders 232 (FIG. 7) to elevate the type Wheel 151 to its extreme upward position (with row 231 thereof in print ing position). Now, with the shaft 173 thus in its extreme rotary position (counterclockwise in FIG. 10 and clockwise in FIG. 12), the sector 281 will be positioned as shown in FIG. 12. Then, as the member 193 is elevated to its extreme upward position, its arm 361 impinges against the edge 393 of the web of the slidable member 295 (FIG. 12), whereupon the resulting pull on the spring 2S2 will cause lever 291 to rotate clockwise (as viewed in FIG. 12) to present the blocking portion 299 into the path of the sector 281 as shown in said FIG. 12. When bail 2&8 is returned to its forward position, the roller 394- iG. 10) on the right end of shaft 249 will strike the end of the rack member 241 to impart reverse or forward movement to the rack 241 to cause gear 242 to be rotated in a clockwise direction, as viewed in FIG. 10, which is counterclockwise in FIG. 12. Now, the sleeve 275 cannot rotate in the counterclockwise direction with the gear 242, as viewed in FIG. 10, because of the fact that the sector 281 impinges against lever 299 and is blocked against rotation thereby. Thus, the pivots 276 of the planetary gears 277 are now fixed, and therefore, the planetary gears 277 rotate with the spur gear 242 through the bevel gear 274 fixedly associated therewith. This rotation of the planetary gears 277 turns the other bevel gear 272 in a clockwise direction, as viewed in FIG. 12. Therefore, since gear 272 is fixedly related to sleeve 271, the detent between ball bearings 282 and groove 289 will be overcome, and the sleeve 271 and shaft 1'73 will be rotated an additional amount in the same (clockwise) direction, instead of being returned to the home position. More specifically, when the type wheel is rotated by rack Zl to its extreme rotary position, it will have been rotated 78 45, as indicated in FIG. 15, to bring the type character thereat into printing position. Now, when the type wheel is advanced an additional amount upon the return movement of rack 241, as above described, it will have been advanced an additional 78 45 or a total of 157 30. However, in the embodiment of the invention herein disclosed, the gear ratio of the two gear sectors 278 and 27% of each planetary gear 277 provides the further additional rotary movement to a 180 detented position. When the member 193 is returned to its lowermost position, its arm 392 will strike arm 293 of lever 291 to rotate said lever counterclockwise (as viewed in PEG. 12) to remove blocking portion 295- out of blockin' relation with the sector 231, and at the same time because of the yield provided by spring lever will become latched in its count rclockwise position benmd the latch portion 297 of slide 295 until a letters unshift code signal is received.

The procedure in response to a letters unshift code signal is similar to that just described in connection with a figures shift code signal, except that the rack memher 239 will be actuated by the bail 248 to cause the gears to rotate in a reverse direction in each analogous instance, and to cause the sector 231 to be blocked by the opposite side (rear side, with reference to FIG. 12) of the blocking lever 291. For example, when rack 239 is first actuated by bail 24-8, gear 242 (FIG. 12) will rotate in a counterclockwise direction and present the-sector 281 behind the blocking portion 299. Then, when rack 2-39 is returned, by roller 3% (FIG. 10) impinging thereon, gear 242 will rotate clockwise, and because the planetary gear pivots 276 are fixed, the gear 272 will ro tate counterclockwise an additional amount to rotate shaft 173 accordingly.

To assist in achieving the additional movement beyond 157 30', a fiat surface 3535 has been provided on the outer peripheral surface of sleeve 271 opposite the groove 281,, as shown in FIG. l3. This flat surface 3&5 acts as 14 a cam surface, which, in conjunction with the ball bearing detents, carries the type wheel positioning shaft 173 and sleeve 271 (and hence type wheel 151) to the detent position.

In FIG. 16 is illustrated an alternate form of differential gearing for the case shift mechanism. In this arrangement, the collar 3tl7 is analogous to collar 273, and the gear 3% is analogous to gear 272. However, the sleeve 3% (comparable to sleeve 275) is provided with a pair of studs 311 positioned angularly thereto to accommodate a pair of planetary gears 312. This arrangement obviates the use of gear sectors (like 278 and 279) of different pitch diameters, and the bevel gears 3&8, 312 and 313 may be so chosen as to give the desired rotational movements to the type wheel.

Having reference to FIG. 7, a clamping device 321 is carried on the type wheel carrier 164, for clamping a cable 322 to said carrier. Cable 322, as shown in FIG. 8, extends around a pair of pulleys 323 (only one of which is shown) appropriately carried on brackets 324 secured to the side frames 16 and 325 of the printer apparatus. Cable 322 is suitably wrapped around a hollow cylinder 326, the ends of said cable 322 being secured thereto. Inside said cylinder 32s and co-axial therewith is a rod 327 fixed at each end to the side frames. Rod 327 is threaded through a coil spring 328, one end of said spring being fastened to said rod, and the other end of the spring being secured to the cylinder, such that, upon rotation of the cylinder 326 during the character spacing operation in a manner to be presently described, the coil spring 328 will be wound to store energy therein to effectuate a carriage return operation. Fixed to the cylinder 326 at the right end thereof (as viewed in PEG. 8) is a spacing ratchet 329.

As previously described, the shaft 135' is rocked cyclically by the cam 133 (PEG. 3). Fixed to the shaft 135 is an arm 331 ing operation. Pivotally connected to the extremity of arm 331 is one end of a link 332, the other end of which is connected pivotally to the vertically directed'arm of a spacing lever 333, mounted on a pivot 334 suitably fixed in the apparatus. Pivotally connected at 335 to the downwardly directed arm of lever 333 is the spacing pawl 336 adapted to be spring pressed against the teeth of the spacing ratchet 329 by a spring (not shown). Thus, when the shaft rocks back and forth once for each printing cycle, the arm 331, through link 332, will oscillate lever $33 to actuate pawl 336 to rotate the cylinder 326 one angular step to cause the cable 322 to advance the type wheel carrier 164 one character space Juxtapositioned (toward the right as viewed in FIG. 8). to the spacing pawl 336 is a detent pawl 337 mountedon a pivot 33% suitably located in the apparatus, and biased by a spring 339. The spacing operation just described is incidental to each character printing operation. However, as will presently appear, a spacing operation may occur independently of a printing operation under the control of the function lever 341 (FIG. 8).

The function levers 152 indicated generally as such in PEG. 7, are specifically identified in FIG. 8 as the space function lever 3 :1, the bell function lever 342, the blank function lever 343, the figures function lever 3 34, the letters function lever 345, the carriage return function lever 3% and the line lead function lever 347. of the function levers terminate in a vertically directed portion 348 (FIG. 7). The line feed function lever 347 is provided in addition thereto with a stepped extremity 349.

Cooperably related to the vertical portion 348 of each function lever is an actuating bail 351 mounted pivotally on a shaft 352. Bail 351 is provided with an arm 353 (best shown in FIG. 17) terminating in a laterally directed stud 354 cooperating With the bifurcated end of an arm 355 clamped to the operating shaft 185, so that, as the shaft 185 rocked cyclically, oscillating motion is (FIG. 17) for controlling the spacl imparted to the bail 351. Thus, upon selection of the line feed function lever 347 (FIG. 7) in well known manner, the portion 348 thereof is presented in the path of the bail 351, and also, the shouldered or stepped extremity of lever 347 will become engaged with the hooked end of a lever 356 carried pivotally by one arm of a line feed bell crank lever 357 mounted on a pivot 358 fixed in the apparatus. Lever 356 is normally biased clockwise by a spring 359 to maintain the end thereof in engaging relation with the shoulder 349. Pivotally carried on the vertical arm of lever 357 is a line feed pawl 361 biased by a spring 362 into engagement with a line feed ratchet 363 fixed to the platen shaft 364. Spring 362 also tends to hold lever 357 against a fixed stop 365. A spring actuated detent 366 is provided to hold the platen 163 against free rotation.

To effectuate the line feed operation, bail 155, when lowered (by link 157, lever 158 and cam 132) will, because of the interengagement between hook 356 and shoulder 349, impart counterclockwise movement to bell crank lever 357 to cause the pawl 361 to rotate the platen one angular step. Simultaneously, the character spacing operation is suppressed in the following manner: Mounted pivotally on the shaft 352 is a space suppression bail 357 having a blade 363 presented in front of all of the portions 348. Bail 367 is also provided with a rearwardly extending arm 369 which cooperates with the laterally disposed extremity 371 of the horizontal arm 372 of a space suppression lever 37f carried freely on the carriage return shaft 373. Said space suppression lever 37% is also provided with an arr-a 3'74 terminating in a laterally directed portion adapted to cooperate with the extremity of the spacing pawl 336, such that when the portion 348 of the line feed lever 347 is interposed between blade 363 and the blade of bail 351, the ensuing rocking motion of shaft 185 will, through arms 355 and 353 cause the bail 351 to actuate the line feed lever 347 leftwardly (PEG-S. 7 and 17) to impart counterclockwise rotation to bail 367 which through its arm 369 will, through arm 372, rotate the space suppression lever 37% clockwise, which in turn, through its arm 374 will raise the spacing pawl 336 out of engagement with the teeth of the ratchet 329, thereby preventing the ensuing reciprocation of pawl 336 from stepping the ratchet 32?.

Also clamped to the operating shaft 185 is a stripper arm 3'75 terminating in a laterally directed portion 376 which cooperates with the hook member ass, such that at a predetermined instant in the line feed operation, the oscillation of arm 375 will cause the hook member 356 to be disengaged from the shoulder portion 349 of the line feed function lever 347.

The carriage return function lever 345 carries pivotally thereon one end of a link 376, the other end of which is connected pivotally to the end of a lever arm 377 pivotally supported on a stud 378 mounted in the side frame 16. Projecting from the pivotal connection between the link 376 and the arm 377 is a stud 3'79 (FIGS. 8 and 17) which cooperates with an arm 381 of a U-shaped bell crank lever 382 clamped to the carriage return shaft 375, the other arm 333 of which terminates in a laterally directed portion adapted to span the extremities of both the spacing pawl 336 and the detent pawl 337.

When the carriage return function lever 345 is selected, it will be permitted, when the bail 155 is raised, to rotate counterclockwise under the influence of its spring 154, to interpose its portion 348 between bail blades 36% and 351. Then, when the operating bail 351 is oscillated, the carriage return function lever 346 will be actuated leftwardly (as viewed in FIG. 17). The link 376, being connected to the lever 346 will also be actuated leftwardly, thereby causing the stud 379 through its camming action with arm 381 to rotate the bail 382 clockwise to thereby cause the laterally directed extremity of arm 333 to lift both of the pawls 337 and 336 away from the ratchet 329. Therefore, the carriage return spring 32.3 is now free to unwind spread;

and effect the return of the type wheel carrier 164 to the left (as viewed in FIG. 8) or beginning of line position. To assure the return of the carrier 164- and the completion of the carriage return operation, a lever arm 384 is clamped to the carriage return shaft 373 (HG. 8), which arm 38 i cooperates with a latch lever 38S mounted pivotally at 386 to a suitable bracket secured to the side frame 325. Lever 385 is normally biased clockwise (as viewed in FIG. 8) by a spring 38?. Arm normally rests on a step 3238 of lever 385. Then, when the carriage return shaft 373 is rocked clockwise (as viewed in P18. 17) by the stud 379, the lever arm 384 is raised away from step 38% and is caused to rest on step 389, due to the clockwise rotation of latch lever 385 by its spring 387. Therefore, the carriage return shaft 373 will be held in its clockwise position until a projection (not shown) on the type wheel carrier lo i impinges against the adjustable screw 3% carried on the latch lever 385, causing lever 385 to rotate counterclockwise sufficiently to disengage the arm 334- from step 339 and return it to step 388, there by permitting the carriage return shaft 373 to return to its normal counterclockwise condition, shown in FIG. 17.

In the performance of certain functions under the control of the function levers 341 to 3 .7, it is desirable to suppress the printing operation. Accordingly, each of said function levers is adapted to cooperate with a print suppression bail member 392 mounted pivotally on a shaft 393 appropriately positioned on brackets 394 secured to plate 13. (Fig. 7). As each of the function levers 341 to 347 is selectively actuated leftwardly (as viewed in FIGS. 7 and 17) by the operating bail 353. through the instrumentality of its projection 34% clockwise rotation is imparted to the bail 392. Bail 392 is provided with an arm 395 (FIG. 7) carrying a stud 3% at its extremity which cooperates with arm 397 of a blocking lever 398 pivoted at 399. Blocking lever 398 is provided with a blocking portion 401 adapted to be swung beneath the pawl 20? to prevent the pawl 269 from becoming disengaged from the printing hammer member 337 as would normally occur during a printing operation, as previously described. Thus, when bail 351 is oscillated pursuant to the selection of a function lever 341 to 347, the function lever, in addition to effecting the function assigned to it, will actuate the bail 395 and arm 397 to suppress, in the manner just described, the printing of a character.

Referring to FIG. 8, it will be observed that the bell function lever 342 is provided with a depending projection 4'82 which cooperates with arm 403 of a striker lever 4&4 pivoted at 495 in the apparatus. Secured to arm 4&3 is a spring 406, the other end of which is anchored to a spring post (not shown). Thus, when the function lever 34-2 is selectively actuated in the manner described in connection with function levers 346 and 347, the lever 4 34 will be rotated clockwise (as viewed in FIG. 8) against the tension of spring 406, such that, when the function lever 342 is returned to normal, the spring 496 will rotate the bell crank 4M counterclockwise with sufficient momentum to cause the striker arm 497 to ring the bell 408.

In response to a blank code signal (which is an allspacing code signal) the function lever 343 is selected and through the instrumentality of projection 348, the lever 343 is actuated to suppress both the printing and spacing operations, in the manner hereinbefore described. However, when the space function lever 341 is selected to'etfect spacing between words, the printing function is suppressed, but due to the notch 4% in the bail blade 36$ (PEG. 8) the bail 367 cannot be operated to suppress spacing, and accordingly. only a spacing operation occurs.

Having reference to FIG. 7, a Figures-Letters shift bar 411 is shown associated with the selector bar 49-1 to 49-5. Referring to FIG. 20, the shift bar 411 is shown as mounted slidably on rods 51 and 4-12. Bar 411 is provided with a detent projection 413 cooperable with the rod 412, to hold, in cooperation with spring 414, the

shift bar 411 in either its fFigures (rightward) position (as shown), or its Letters (leftward) position. The bar 411 is provided on its bottom edge with notches and wards, so thatin the Letters position the function levers for example 343, will not be blocked against selective operation, but will be blocked in the -Figures position of bar 411. Function levers 344 and 34 are provided with facilities to suppress printing and spacing. -When selected, the Figures function lever 344will coact with cam surface 415 of the depending projection 416 on bar 411 to move the bar 411' to its rightward position and locate said notches above the function levers to permit their selective operation. On the other hand, the Letters function lever 345, when selected, will c'oact with the cam surface 417 to move the bar 411 leftwardly to position the wards above the function levers to prevent selection thereof. For example, if the bell signal is Figs. S or any other non-printing upper case character) then the Figs. code signal will place the bar 411 in the Figures position to unblock the function lever 342, which when operated to ring the bell as previously described, will also suppress the printing and spacing operation. However, in the Letters position of bar 411, the function lever 342 will be blocked against selection by the wards on bar 411, printing of the character S can be eifected.

-In FIG. 18 is shown a device for automatically suppressing the spacing operation after the type wheel carriage 164 has reached the end of the line and the carriage return signal has been lost, thus of the spacing mechanism. Appropriately mounted pivotally on a pivot 418 is a bell crank lever 419, the vertical arm 4211 ofwhich is adapted to cooperate with the carriage 164. The horizontal arm sea of lever dlhcooperates with a vertically slidable member 4 23. suitably guided, and mounted on shaft 352. The upper end of slidable member 423 is aligned with the vertical projections 348 of the function levers (FIG. 17). Lever 4191's normally biased counterclockwise by a spring 424, and slidable member 423 is normally held against the horizontal arm 422 by a spring 425 coiled about the pivot 18. Therefore, if the carriage 164 has reachedthe .end of the line, and a carriage return signal has been lost, the next spacing operation will cause the lever d l9 to be rotated clockwise snfiiciently to raise the slidable member e23 to interpose the upper end thereof between bail bladesl'i efi and 351, so that the spacing operation will. be suppressed thereafter until the next carriage returnsignal is received, or the trouble is corrected manually, whereupon the carriage 164 will be returned, and the slidable member 423 will be lowered to its normalpcsition.

The inking ribbon 426 isadapted to be moved intorand outof the printing positionto effect visible printing, by means of a pair of lever arms 4 27, one located at each end of the platen 163. Arms 4277 are mounted on individual pivots428, and are providedwith guide slots .429 into which are operable individual studs 431 carried on an arm 432clamped to the operating shaft 185, so that upon each oscillation oftshaft 185, the leyer arms 427 are rocked to move the ribbon 425 to and fro in front of the platen 163.

The type wheel carriage 164 near the end of its carriage return moveme t strikesgone arm of a dash pot lever 432 mounted pivotally on a bracket .433 secured to side frame 325, theotherarmpf which is connected to the piston 4-34 of a dash pot 435. Thus the movement of carriage .164 is cushioned in .well known manner.

In FIG. 19 is shownan alternate form of line feed mechanism, wherein the line feed operation is executed in a-more direct manner fromthe operating shaft 185.

Fixed-to shaft 185 is a bell crank lever 436, the horizental arm of which terminates in a laterally-directed pertien 437 which cooperates with a shoulder 438 on a leverarm 43-9 depending from and pivotally connected In the latter position, the

precluding the jamming mountedon a fixed pivot stud 442. Carried pivotally at the end of the arm 441 is a line feed pawl 443 adapted to cooperate with a line feed ratchet 3'63 fixed to the shaft 364 of platen 163'. Pawl M3 .is normally biased counterclockwise into engagement with ratchet 36 3 by a spring dlddistended between pawl 443 and arm 439 so as to normally bias arm 439 in a clockwise direction against the laterally directed end 445 of the downwardly directed arm of bell crank lever 436. Normally, when the linefeed function lever is in its unselected position (solid line position in FIG. 19) the arm 439 will follow the lateral portion 445 of lever 436 in its oscillation without having any efiect on the line feed lever arm 441. However, when'the line feed function lever is in its selected position (dotted line position in FIG. l9) the laterally directed end 446 of arm 439 will strike the end of lever 3'37 and be blocked thereby against further clockwise movement by spring 4 34, so as to allow the end 437 of lever 43610 strike against the shoulder 438 of arm 4-39 to thereby force arm 437 in a down; ward direction to impart counterclockwise rotation to line feed arm 441 and hence cause the pawl 443 to rotate the line feed ratchet one angular step.

Although a particular embodimentof the invention is to a line feed leverarm e41 shown in the drawings and described in the foregoing specification, it will be understood that the invention is not limited to that specific embodiment, but is capable of modification and rearrangement, and substitution of parts and elements without departing from the scope of the invention. i

What is claimed is:

1. In a printing telegraph apparatus, a platen, a rotatable type carrier, a movably mounted framefor supporting said type carrier adjacent said platen, yieldable means normally holding out of engagement with said movement 'of said frame to engagement with the platen, and a print hammer disposed on the opposite side of the type carrier from the platen and in line with the type carrier andthe platen, and means for causing said print hammer to move along said line and strike the frame to drive the type carrier platen and accommodating bring the type carrier into against the platen.

2. In aprintingtelegraph apparatus, a platen, a rotatable type carrier havinga plurality .of rows of characters thereon, a pivotally mounted type carrier frame for supporting said type carrier adjacent said platen, a support for said frame displaced from the axis of rotation of said type carrier Fahd displaced from the face of said platen, and a printhammer supported adjacent said frame on the si de opposite to said platen, said hammer operable to strike said frame and to cause said frame to rotate about its support and carrysaid type carrier in an orbital path about said frame support and into engagement with said platen.

3. In a printing telegraphjapparatus, a platen, a pivotally mounted bracket havi g a 'Llrshaped portion with the open end thereof eonfrontingsaid platen, a support for said bracket displaced from'said platen, a rotatable typewheel journalled in the 'U-shaped portion of said bracket for rotation about its own axis and supported for orbital movement aboutsaid bracket support, and a printinghammer supported adjacent'isaid bracket and operable upon the receipt of any of a plurality of predetermined signals by said printing apparatus to strike said closed part of said- U-shaped portion of said bracket to. pivotally move said bracket and said typewheel about said bracket support to bring said typewheel into printing engagement with said platen.

'4. "In-a printing telegraph apparatus, a signal responsive selector mechanism, a printing platen, a rotatable indexing shaft having a plurality of discrete rotative positionsselectable by saidselector mechanism, a type- Wheelcarrier pivotally mounted on said shaft, a typesaid frame and type carrier Wheel rotatably supported by said carrier in spaced relation to said indexing shaft and having its axis parallel to that of said shaft, gearing interconnecting said shaft and said typewheel to cause indexing of said typewheel by said shaft in accordance with selected rotative positions of said shaft, and means for rocking said typewheel carrier about said shaft to effect orbital movement of said typewheel about said shaft, until arrested by the printing platen.

5. In a printing telegraph apparatus, a signal responsive selector mechanism, a printing platen, a rotatable indexing shaft having a plurality of discrete rotative positions selectable by said selector mechanism, a typewheel carrier pivotally mounted on said shaft, a typewheel rotatably supported by said carrier in spaced relation to said indexing shaft and having its axis parallel to that of said shaft, gearing interconnecting said shaft and said typewheel to cause indexing of said typewheel by said shaft in accordance with selected rotative positions of said shaft to selectively present characters in confronting relation to said platen, and means for rocking said typewheel carrier about said shaft to effect orbital movement of the typewheel about the shaft until arrested by the printing platen, said gearing maintaining confronting relation of the selected characters with the platen during the rocking of the typewheel carrier.

6. In a printing telegraph apparatus, a signal responsive selector mechanism, a printing platen, a rotatable indexing shaft having a plurality of discrete rotative positions selectable by said selector mechanism, a typewheel carrier pivotally mounted on said shaft, a typewheel rotatably supported by said carrier in spaced relation to said indexing shaft and having its axis parallel to that of said shaft, gearing interconnecting said shaft and said typewheel to cause indexing of said typewheel by said shaft in accordance with selected rotative positions of said shaft to orient said typewheel with respect to said platen, and means for rocking the typewheel carrier about the shaft to effect orbital movement of the typewheel about the shaft until arrested by the printing platen, said gearing retaining the orientation of said typewheel with respect to said platen during the rocking of said typewheel carrier.

In a printing telegraph apparatus, a printing platen, a signal responsive selector mechanism, a rotatable indexing shaft having a plurality of discrete rotative positions selectable by said selector mechanism, a typewheel carrier pivotally mounted on said shaft, a typewheel rotatably supported by said carrier in spaced relation to said indexing shaft and having its axis parallel to that of said shaft, gearing interconnecting said shaft and said typewheel including a gear secured to said shaft, a gear secured to said typewheel and an intervening idler gear to cause indexing of said typewheel by said shaft in accordance with selected rotative positions of said shaft to orient said typewheel with respect to said platen, and means for rocking said typewheel carrier about said shaft to effect orbital movement of said typewheel about said shaft until arrested by said platen, said gearing maintaining the orientation of said typewheel with respect to said platen during the rocking movement of said carrier.

8. In a printing telegraph apparatus, a printing platen, a signal responsive selector mechanism, a rotatable indexing shaft having a plurality of discrete rotative positions selectable by said selector mechanism, a typewheel carrier pivotally mounted on said shaft, 21 typewheel ro tatably supported by said carrier in spaced relation to said indexing shaft and having its axis parallel to that of said shaft, gearing interconnecting said shaft and said typewheel including a gear secured to said shaft, a gear secured to said typewheel and an intervening idler gear to cause indexing of said typewheel by said shaft in accordance with selected rotative positions of said shaft to orient said typewheel with respect to said platen, and means for rocking said typewheel carrier about said shaft to effect orbital movement of said typewheel about said shaft until arrested by said platen, said idler gear adapted to roll around said gear secured to said shaft to impart rotation, in a direction opposite to the direction of said rocking movement, to said typewheel through said gear secured to said typewheel and thereby maintain the orientation of said typewheel with respect to said platen.

9. In a printing telegraph apparatus, a signal respon sive selector mechanism, a rotatable indexing shaft having a plurality of discrete rotative positions selectable by said selector mechanism, a typewheel carrier pivotally mounted on said shaft, a typewheel rotatably supported by said carrier in spaced relation to said indexing shaft and having its axis parallel to that of said shaft, gearing interconnecting said shaft and said typewheel to cause indexing of said typewheel by said shaft in accordance with selected rotative positions of said shaft, a printing platen, and a print hammer operable to rock said typewheel carrier about said shaft to effect orbital movement of said typewheel about said shaft until arrested by said platen.

10. in a printing telegraph apparatus, a signal responsive selector mechanism, a cylindrical printing platen, a rotatable indexing shaft having a plurality of discrete rotative positions selectable by said selector mechanism, a typewheel carrier pivotally mounted on said shaft, :1 typewheel rotatably supported by said carrier in spaced relation to said indexing shaft and having its axis parallel to that of said shaft, gearing interconnecting said shaft and said typewheel to cause indexing of said typewheel by said shaft in accordance with selected rotative positions of said shaft, an arm rigidly associated with said typewheel carrier and overlying said typewheel on the opposite side of said typewheel from said platen, and a print hammer operable to strike said and and rock said carrier about said shaft to effect orbital movement of said typewheel about said shaft until arrested by said platen. I

11. In a printing telegraph apparatus, a signal respori sive selector mechanism, a cylindrical printing platen, a rotatable indexing shaft having a plurality of discrete rotative positions selectable by said selector mechanism, a typewheel carrier pivotally mounted on said shaft, a typewheel rotatably supported by said carrier in space relation to said indexing shaft and having its axis paralle to that of said shaft, gearing interconnecting said shaft and said typewheel to cause indexing of said typewheel by said shaft in accordance with selected rotative positions of said shaft, an arm rigidly associated with said typewheel carrier and overlying said typewheel on the opposite side of said typewheel from said platen, and a print hammer operable through an arc confined to a plane normal to the axis of said platen to strike said arm and rock the carrier about said shaft to efiect orbital movement of said typewheel about the shaft until arrested by the platen.

12. In a printing telegraph apparatus, a signal responsive selector mechanism, a cylindrical printing platen, a rotatable indexing shaft having a plurality of discrete rotative positions selectable by said selector mechanism, a typewheel carrier pivotally mounted on said shaft, 2. typewheel rotatably supported by said carrier in spaced relation to said indexing shaft and having its axis parallel to that of said shaft, gearing interconnecting said shaft and said typewheel to cause indexing of said typewheel by said shaft in accordance with selected rotative positions of said shaft, an arm rigidly associated with said typewheel carrier and overlying said typewheel on the opposite side of said typewheel from said platen, and a print hammer operable to apply a striking blow to said arm substantially in a direct line with the printing point for the character selected by indexing of said shaft and to rock the carrier about said shaft to effect orbital move.

21 ment of said typewheel about the shaft until arrested by the platen.

13. In a printing telegraph apparatus, a signal responsive selector mechanism, a cylindrical printing platen, a rotatable indexing shaft having a plurality of discrete rotative positions selectable by said selector mechanism, a typewheel carrier pivotally mounted on said shaft, a typewheel rotatably supported by said carrier in spaced relation to said indexing shaft and having its axis parallel to that of said shaft and defining with the axis of said shaft a plane substantially parallel to the axis of said platen, gearing interconnecting said shaft and said typewheel to cause indexing of said typewheel by said shaft in accordance with selected rotative positions of said shaft, an arm rigidly associated with said typewheel carrier and overlying said typewheel on the opposite side of said typewheel from said platen, and a print hammer operable to strike said arm and rock said carrier about said shaft to effect orbital movement of said typewheel about said shaft until arrested by said platen.

14. In a page printing telegraph apparatus, a cylindrical printing platen, a shaft so disposed relative to said platen that a plane containing the axis of said shaft can cross the axis of said platen at right angles, a frame pivotally mounted on said shaft, a typewheel rotatably supported by said frame with its axis in spaced relation and parallel to the axis of said shaft, and a print hammer operable to rock said frame about the shaft and impart orbital movement to said typewheel about the shaft and into engagement with the platen in a relation of tangency of a line longitudinally of the surface of the typewheel at the point of engagement to the surface of the platen.

15. In a printing telegraph apparatus, a platen, a type carrier having a plurality of horizontal rows of characters formed thereon, said type carrier being provided with at least two groups of characters with the center of one group confronting said platen, signal responsive means, elevator means controlled by said signal responsive means for elevating said type carrier to select a horizontal row of characters, rotating means controlled by said signal responsive means for rotating said type wheel to select a character in a horizontal row, shift means having differential facilities for rotating said type carrier to move the center of the other of said group of characters into confronting relation with said platen and means effective in a predetermined elevational and rotational position of said type carrier to operate said differential facilities.

16. In a printing telegraph apparatus, a platen, a type carrier having a plurality of horizontal rows of characters formed thereon, said type carrier being provided with at least two groups of characters with the center of one group confronting said platen, signal responsive means, elevator means controlled by said signal responsive means for elevating said type carrier to select a horizontal row of characters, rotating means controlled by said signal responsive means for rotating said type wheel to select a character in a row, inhibiting means carried by said elevator means, shift means having differential facilities for rotating said type carrier to move the center of the other of said group of characters into confronting rela-.

tion with said platen and impinging means carried by said shift means and being cooperatively effective with said inhibiting means, in a predetermined elevational and rotational position of said type carrier, to operate said differential facilities.

17. In a printing telegraph apparatus, a platen, a type wheel supported in spaced relation with respect to said platen and having a plurality of circumferential rows of characters formed thereon with the characters being divided into an upper case character group and a lower case character group, said character groups being arranged on opposite semi-circumferential faces of said type wheel with the center of one of said semi-circumferentially arranged faces confronting said platen, signal responsive means, elevating means controlled by said signal responsive means for axially positioning said type Wheel with respect to said platen to select a circumferential row of characters, rotating means controlled by said signal responsive means for rotating said type wheel to select a character in a circumferential row, shift means having differential facilities, impinging means carried by said rotating means and a blocking member carried by said elevating means and presentable for engagement by said impinging means upon elevation of said type wheel to a predetermined axial position and rotation of said type wheel into a predetermined rotative position to cause operation of said differential facilities to rotate said type wheel to present the other of said semi-circumferential faces in confronting'relation With said platen and thereby accomplish a case shift operation.

2,339,313 Zenner Jan. 18, 1944 

